EP0907041B1 - Rollenkettenrad mit Zufallsauswahl. - Google Patents

Rollenkettenrad mit Zufallsauswahl. Download PDF

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Publication number
EP0907041B1
EP0907041B1 EP98307854A EP98307854A EP0907041B1 EP 0907041 B1 EP0907041 B1 EP 0907041B1 EP 98307854 A EP98307854 A EP 98307854A EP 98307854 A EP98307854 A EP 98307854A EP 0907041 B1 EP0907041 B1 EP 0907041B1
Authority
EP
European Patent Office
Prior art keywords
sprocket
radius
root
roots
roller
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP98307854A
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English (en)
French (fr)
Other versions
EP0907041A1 (de
Inventor
Timothy J Ledvina
John A. Hummel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BorgWarner Inc
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BorgWarner Inc
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Filing date
Publication date
Application filed by BorgWarner Inc filed Critical BorgWarner Inc
Publication of EP0907041A1 publication Critical patent/EP0907041A1/de
Application granted granted Critical
Publication of EP0907041B1 publication Critical patent/EP0907041B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/30—Chain-wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/06—Gearings for conveying rotary motion by endless flexible members with chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F16H2055/086—Silent gear profiles

Definitions

  • the present invention relates to a sprocket for roller chain that is designed to modulate the engagement frequency of a conventional roller chain without introducing harsh impact loads on the rollers or bushings.
  • the present invention modulates the roller engagement by randomizing the radial seating position of the roller while maintaining a constant chordal length between the seated rollers.
  • the root diameters of the sprocket roots are randomized around the circumference of the sprocket.
  • Silent chains have previously used randomized sprockets in an attempt to modulate the engagement frequency of the chain links with the sprocket.
  • the randomization of the sprocket is conventionally achieved by relieving, or removing, a small amount of material from the sides of some of the sprocket teeth.
  • the relieved sprocket teeth are typically interspersed with the non-relieved sprocket teeth in a predetermined pattern around the sprocket.
  • the resulting chain drive produced a modulation of noise from engagement at the pitch frequency.
  • An example of such a chain is shown in US-A-3,377,875.
  • roller chain that utilized such a sprocket with relieved teeth would have some rollers subjected to higher impact loads, which would lead to premature fatigue failure of the rollers. Since roller fatigue is one of the prime failure modes of high speed roller chain drives, this problem presents a major obstacle to the adoption of conventional random sprockets for roller chains.
  • US-A- 3,448,629 is directed to reduction of chain impact in a roller chain by modifying the bottom diameter of the sprocket root from the theoretically correct bottom diameter relative to a given chain and widening the gap between adjacent teeth of the sprocket sufficiently to allow the modified sprockets to mesh with the chain.
  • This sprocket does not provide a randomization of the root diameters of the sprocket roots around the circumference of the sprocket.
  • PCT International Publication Number WO 97/11292 published March 27, 1997, discloses a roller chain timing drive directed to reduction of impact noise by thinning the teeth and elongating the root land between each pair of teeth.
  • the root land is elongated resulting in a reduced thickness of the teeth as measured across itself from a drive flank to a coast flank. The result is the maintenance of contact of all rollers wrapped around a sprocket throughout the design life of the chain.
  • Another chain and sprocket power transmitting mechanism is disclosed in US-A-4168 634 in which the driven sprocket includes a first set of conventional involute teeth and a second set of modified teeth disposed in random patterns, the modified teeth having the flanks on their trailing sides relieved a predetermined amount and the roots adjacent thereto formed on a diameter a predetermined amount larger than the root diameter of the first set of conventional teeth so as to improve noise reduction characteristics.
  • the present invention is directed to varying the radial seating positions of the roller while maintaining a constant chordal dimension between seated rollers. This variation or randomization provides a noise modulation effect whilst avoiding the negative effects of high impact which arise in conventional randomized sprockets.
  • the present invention provides a roller chain and sprocket drive system, comprising: a roller chain having a plurality of pairs of interleaved links, said pairs of links being interconnected by pivot pins, each of said pivot pins containing a generally circular roller member freely rotatable about said pins, said roller chain having a chordal pitch defined as the distance between centers of adjacent pivot pins, a generally circular sprocket having a plurality of teeth spaced about its periphery, said sprocket including roots located between pairs of adjacent teeth for receiving said rollers, said sprocket pitches defined 'as the distance between the center of adjacent pivot pins seated in adjacent roots, each of said roots having a root radius defined as the distance between the center of said sprocket and the point along said root closest to the sprocket center in the radial direction; characterised in that:
  • chordal pitch distance is defined as the distance between the centers of adjacent rollers in the chain.
  • the roller chain and sprocket drive assembly includes a sprocket with a plurality of roots with the first root radius and a plurality of roots with the second root radius.
  • the roots having the first root radius are arranged with the roots having the second root in a predetermined irregular pattern about the sprocket.
  • irregularly arranged it is meant that the pattern is staggered between first and second radii, and not a pure alternating pattern between first and second radii.
  • the roller chain and sprocket drive may also advantageously include a plurality of roots that have a third root radius, with the third root radius being less than the second root radius.
  • the first, second and third root radii define maximum, nominal and minimum root radii around the sprocket.
  • the roots having the third root radius are then randomly arranged with the roots having the first root radius and the roots having the second root radius in a predetermined pattern about the sprocket periphery.
  • the predetermined pattern is also preferably arranged so that at least one root having the second root radius, or nominal radius, is always between a root having the first radius, or maximum radius, and a root having the third radius, or minimum radius.
  • the present invention is directed to a random sprocket for a roller chain in which the radial and circumferential positions of the sprocket teeth are adjusted slightly (or randomized) from their conventional uniform spacing. In this manner, the radial seating positions of the rollers are varied between sprocket teeth while the pitch distance (or chordal distance) between seated rollers remains constant.
  • an average seating radius is first determined so that the starting and ending positions on the sprocket join smoothly.
  • the adjustment in seating radius is such that the rollers seat in the root between the sprocket teeth at a radial distance of either a nominal seating radius, an upper (maximum) seating radius, or at a lower (minimum) seating radius.
  • the roller seat between the sprocket teeth at a radial distance of either a maximum seating radius or at a minimum seating radius.
  • the roller seating positions between sprocket teeth are randomly varied around the sprocket in a predetermined pattern.
  • the pattern preferably locates a roller with a nominal seating radius before and after each roller with a maximum or minimum seating radius. When only two seating radii are utilized, the pattern of seating radii is randomized rather than alternated between maximum and minimum.
  • roller seating radii results in a modulation of the timing of successive impacts of the rollers with the sprockets.
  • a sprocket 10 is shown with rollers 12, 14, 16 of an associated roller chain seated between two teeth 18, 20.
  • the sprocket is characterized by dimensions of an outer diameter (OD), a root diameter (RD) and a pitch diameter (PD).
  • the outer diameter is the dimension from the sprocket center point to the outermost location on a tooth.
  • the root diameter is the dimension from the sprocket center point to the lowermost location in the root between two adjacent sprocket teeth.
  • the pitch diameter is the dimension from the sprocket center point to the pitch circle of the sprocket.
  • Each roller also has a diameter of dimension D.
  • the present invention is directed to the concept that very small changes in the angular displacement from root to root can have a large effect on the timing of the roller engagement with the seat and therefore a large effect on generation of impact noise.
  • Impact noise includes both a radial component from the roller or bushing striking the bottom of the root as well as a tangential component from the roller or bushing striking the side of the root (or tooth).
  • the present invention is primarily directed to the randomization of that radial component, in contrast to the modification of the tangential component in some prior art sprockets which relieve the side of the tooth.
  • the pitch distance (or chordal length) between seated rollers remains constant. Maintaining a constant chordal length reduces the impact load of the rollers against the teeth.
  • the variation in the seating position from tooth to tooth results in a modulation of the timing of successive impacts. This modulation reduces the pitch frequency noise produced by the chain drive.
  • the effective tooth thickness as measured at an arbitrary point along the tooth will vary from tooth to tooth around the sprocket as a result of the modification of the root diameters.
  • the geometry or shape of the root or pocket which holds the roller in its seated position is maintained generally the same from tooth to tooth.
  • the design of the present invention is directed to maintaining the engagement (or seating) of the roller with the root of the sprocket, but changing the position of the root radially from tooth to tooth.
  • the modification of the present invention is directed to the root location or position and not to the tooth profile.
  • a pattern of variation in seating position is chosen as the teeth progress around the sprocket.
  • the pattern is random. That is, it varies irregularly around the sprocket.
  • the pattern does not contain any abrupt transitions from the upper seating or the lower seating positions to the other extreme position without passing through the nominal seating position for at least one tooth. Avoidance of abrupt transitions should contribute to the smooth running of the chain and reduce the generation of mechanical noise and reduce wear on the rollers.
  • the location of the seating radius of each root (or the space between sprocket teeth in which the rollers seat) must be determined. While locating the seating position of each roller, the pitch distance between seated rollers must remain constant.
  • a starting value for the mean pitch radius R2 is first chosen.
  • the value of the pitch distance, or the nominal pitch radius 1 ⁇ 2 x P x 1/sin(180/N), where N is the number of sprocket teeth, is a convenient choice.
  • a starting value for R2 may be the pitch distance P1 between adjacent seated rollers on the associated chain divided by the quantity 2 x sin(180/N).
  • the minimum and maximum pitch radii values are then calculated from the mean pitch radius value.
  • the minimum, or R1 is calculated by subtracting one-half the value of the peak-to-peak pitch radius variation (Delta) from R2.
  • the maximum, or R3, is calculated by adding one-half the value of the peak-to-peak pitch radius variation (Delta) to R2.
  • the first roller center is then located at top dead center of the sprocket at a distance R2 from the sprocket center.
  • the next adjacent roller center is then located so that it is a constant chordal distance P (or the nominal pitch value) from the first roller center and is at a radial distance R1, R2 or R3 from the sprocket center point, depending on the chosen random pattern.
  • the next adjacent roller is then located so that it is a constant chordal distance P from the center of the second roller and is a distance R1, R2 or R3 from the sprocket center point, depending on the chosen random pattern.
  • the variation between the maximum and minimum was arbitrarily established at 1 mm.
  • the differences in root radius were then set at 1 ⁇ 2 mm or 1/4 mm. Other radii differences may be utilized depending on sprocket size as well as other considerations.
  • rollers 12 and 14 are separated by pitch distance P1 and rollers 14 and 16 are separated by pitch distance P2.
  • P1 is the same as P2, and the remaining pitch distances of the seated rollers around the sprocket are also the same distance.
  • the rollers are seated at different distances from the center point (C) of the sprocket 10. For example, roller 12 is seated at radius R1, roller 14 is seated at radius R2 and roller 16 is seated at radius R1.
  • the chordal pitch distance between the seated first roller and the seated last roller must also equal the nominal pitch, or P. If the chordal pitch distance is not the same as the other seated rollers, then the mean pitch radius R2 must be increased or decreased and the sprocket profile regenerated.
  • the sprocket teeth are positioned so that the radial position of each root or seat is located with the desired clearance between the seat and its mating roller, and such that the tooth space center line is coincident with the radial line from the sprocket center to the mating roller center.
  • the final sprocket profile will likely require the use of blend radii between adjacent teeth.
  • a sprocket profile has been provided in which the distances between the centers of the seated rollers (or the pitch distance or chordal distance) remains constant around the sprocket while the location of the seat of each roller varies so that the center of the associated roller is located on an arc of one of three radii distance from the center point of the sprocket.
  • the present invention has application in bushing chain in which bushings contact the sprocket teeth directly without rollers on the outsides of the bushings.
  • the present invention also has application to silent chains and sprockets in which the impacts of the silent chain links with the sprockets can be modified in the same manner as described above.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Rollers For Roller Conveyors For Transfer (AREA)

Claims (6)

  1. Rollenketten-Kettenrad-Antriebssystem mit
       einer Rollenkette mit einer Vielzahl von Paaren ineinandergreifender Glieder, wobei die Gliederpaare durch Schwenkzapfen verbunden sind, jeder der Schwenkzapfen einen allgemein kreisförmigen Rollenkörper (12, 14, 16) enthält, der um die Zapfen frei drehbar ist, und die Rollenkette eine Sehnenteilung (P1, P2) hat, die als Abstand zwischen den Mittelpunkten benachbarter Schwenkzapfen definiert ist,
       einem allgemein kreisförmigen Kettenrad (10), das eine Vielzahl von Zähnen (18, 20) verteilt um seinen Umfang hat, wobei das Kettenrad (10) Zwischenräume zwischen Paaren benachbarter Zähne (18, 20) zur Aufnahme der Rollen hat und die Kettenradteilungen als der Abstand zwischen den Mittelpunkten benachbarter Schwenkzapfen, die in benachbarten Zwischenräumen angeordnet sind, definiert ist,
       wobei jeder der Zwischenräume einen Zwischenraumradius (RD) hat, der als Abstand zwischen dem Mittelpunkt des Kettenrades und demjenigen Punkt längs des Zwischenraumes definiert ist, der dem Kettenradmittelpunkt in radialer Richtung am nächsten liegt, und mindestens einer der Zwischenräume einen ersten Zwischenraumradius hat,
       dadurch gekennzeichnet, dass:
    mindestens einer der Zwischenräume einen zweiten Zwischenraumradius hat, der kleiner als der erste Zwischenraumradius ist, und
    die Trennung zwischen benachbarten Zwischenräumen des Kettenrades (10) in Umfangsrichtung sich mit Änderungen in den Zwischenraumradien der besagten benachbarten Zwischenräume so ändert, dass die Teilung benachbarter Zwischenräume im wesentlichen gleich der Sehnenteilung der Kette um das gesamte Kettenrad herum ist.
  2. Rollenketten-Kettenrad-Antriebssystem nach Anspruch 1, bei dem mehrere der Zwischenräume den ersten Zwischenraumradius haben und mehrere der Zwischenräume den zweiten Zwischenraumradius haben, wobei die Zwischenräume mit den ersten und zweiten Radien in einem vorgegebenen unregelmäßigen Muster um den Umfang des Kettenrades 10 herum angeordnet sind.
  3. Rollenketten-Kettenrad-Antriebssystem nach Anspruch 1 oder 2, das ferner mehrere Zwischenräume mit einem dritten Zwischenraumradius hat, wobei der dritte Zwischenraumradius kleiner als der zweite Zwischenraumradius ist.
  4. Rollenketten-Kettenrad-Antriebssystem nach Anspruch 3, bei dem die Zwischenräume mit dem dritten Zwischenraumradius in Zufallsverteilung bezüglich der Zwischenräume mit dem ersten Zwischenraumradius und der Zwischenräume mit dem zweiten Zwischenraumradius in einem vorgegebenen unregelmäßigen Muster um den Umfang des Kettenrades herum angeordnet sind.
  5. Rollenketten-Kettenrad-Antriebssystem nach Anspruch 4, bei dem das vorgegebene Muster so ausgebildet ist, dass mindestens ein Zwischenraum mit dem zweiten Zwischenraumradius immer zwischen einem Zwischenraum mit dem ersten Radius und einem Zwischenraum mit dem dritten Radius angeordnet ist.
  6. Rollenketten-Kettenrad-Antriebssystem nach Anspruch 4 oder 5, bei dem das Muster teilweise die folgende Abfolge von Zwischenraumradien hat: erster Radius, zweiter Radius, dritter Radius, dritter Radius, zweiter Radius, erster Radius.
EP98307854A 1997-10-03 1998-09-28 Rollenkettenrad mit Zufallsauswahl. Expired - Lifetime EP0907041B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US6080697P 1997-10-03 1997-10-03
US60806P 1997-10-03

Publications (2)

Publication Number Publication Date
EP0907041A1 EP0907041A1 (de) 1999-04-07
EP0907041B1 true EP0907041B1 (de) 2002-08-28

Family

ID=22031873

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98307854A Expired - Lifetime EP0907041B1 (de) 1997-10-03 1998-09-28 Rollenkettenrad mit Zufallsauswahl.

Country Status (7)

Country Link
US (1) US6155943A (de)
EP (1) EP0907041B1 (de)
JP (1) JP4321891B2 (de)
CN (1) CN1129723C (de)
CA (1) CA2246131C (de)
DE (1) DE69807407T2 (de)
ES (1) ES2183293T3 (de)

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US6213905B1 (en) * 1999-07-01 2001-04-10 Borgwarner Inc. Roller chain sprockets oriented to minimize strand length variation
JP2001130586A (ja) * 1999-11-09 2001-05-15 Fuji Seal Inc 口栓付きパウチ
EP1235003A1 (de) 2001-02-23 2002-08-28 Morse Tec Europe S.p.A. Rollenkettenrad mit unterschiedlichen Zahnprofilen auf dem gleichem Kettenrad
US7125356B2 (en) * 2001-11-06 2006-10-24 Borgwarner Inc. Tension-reducing random sprocket
DE10237277A1 (de) 2002-08-14 2004-03-04 Bosch Rexroth Ag Antriebseinheit für ein Fördermittel
JP3749904B2 (ja) * 2003-06-16 2006-03-01 株式会社スギノテクノ ローラチェーン用スプロケット
JP3886130B2 (ja) * 2003-07-04 2007-02-28 株式会社椿本チエイン チェーン用スプロケット
DE20319172U1 (de) 2003-09-18 2004-04-22 Litens Automotive Partnership, Woodbridge Nicht kreisförmige Rotationskomponente
JP4508616B2 (ja) * 2003-11-28 2010-07-21 株式会社椿本チエイン ローラチェーン伝動装置
US20080256827A1 (en) * 2004-09-14 2008-10-23 Tripod, L.L.C. Sole Unit for Footwear and Footwear Incorporating Same
US8202185B2 (en) * 2004-10-06 2012-06-19 Borgwarner Inc. Random elastomer cushion rings for a chain sprocket
US20060073927A1 (en) * 2004-10-06 2006-04-06 Borgwarner Inc. Elastomer cushion ring for a random tooth roller chain sprocket
US7500928B2 (en) * 2005-01-20 2009-03-10 Borgwarner Inc. Randomized chain system
US20070270260A1 (en) * 2006-05-17 2007-11-22 Latham Andrew V Hub carrier with interchangeable sprockets having different teeth configurations
JP2008019881A (ja) * 2006-07-10 2008-01-31 Tsubakimoto Chain Co チェーン伝動装置
DE102006034364B4 (de) 2006-07-25 2021-07-29 JOH. WINKLHOFER & SÖHNE GMBH & Co. KG Kettenrad mit alternierenden Teilungsabständen
DE102006046520A1 (de) * 2006-09-29 2008-04-03 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Geräuscharmer Kettentrieb
WO2008156483A1 (en) * 2007-06-20 2008-12-24 Borgwarner Inc. Resonance tension reducing sprocket with combined radial variation and sprocket wrap
JP2010540858A (ja) * 2007-09-28 2010-12-24 ボーグワーナー・インコーポレーテッド チェーンおよびスプロケットシステム内の複数の張力低減スプロケット
JP4235242B1 (ja) * 2007-12-26 2009-03-11 株式会社椿本チエイン タイミングチェーンドライブ装置
WO2009111219A2 (en) * 2008-03-06 2009-09-11 Borgwarner Inc. Sprocket randomization for enhanced nvh control
US7823990B2 (en) * 2008-08-27 2010-11-02 Caterpillar Inc Sprocketed idler assembly
JP5009273B2 (ja) * 2008-12-02 2012-08-22 株式会社椿本チエイン タイミングチェーンドライブ装置
CN102308123B (zh) * 2009-02-06 2013-11-06 谢夫勒科技股份两合公司 随机滚子链链轮和制造链轮的方法
US20110312456A1 (en) * 2010-06-17 2011-12-22 David Earle Bicycle Sprocket
US20170191558A1 (en) * 2014-05-29 2017-07-06 Miranda & Irmaco, Lda. Drivetrain system and use thereof
EP3390864B1 (de) * 2015-12-09 2023-06-07 BorgWarner Inc. Willkürliches zahnrad mit nicht-prävalenter ordnung
JP2018001773A (ja) * 2016-06-27 2018-01-11 株式会社シマノ 自転車用スプロケット、及び自転車用スプロケット組立体
JP6955157B2 (ja) * 2017-11-06 2021-10-27 株式会社椿本チエイン スプロケット及び伝動機構
JP7011166B2 (ja) * 2018-03-30 2022-01-26 株式会社椿本チエイン スプロケット及び伝動機構
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Also Published As

Publication number Publication date
JPH11218199A (ja) 1999-08-10
DE69807407T2 (de) 2003-01-09
JP4321891B2 (ja) 2009-08-26
ES2183293T3 (es) 2003-03-16
CN1214421A (zh) 1999-04-21
EP0907041A1 (de) 1999-04-07
CA2246131C (en) 2007-06-05
CN1129723C (zh) 2003-12-03
DE69807407D1 (de) 2002-10-02
CA2246131A1 (en) 1999-04-03
US6155943A (en) 2000-12-05

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